Automatically controlled pneumatically powered lubricator



7 AUTOMATICALLY CONTROLLED PNEUMATICALLY POWERED LUBRICA'DOR Filedse t.8, 1955 F. G. SCHWEISTHAL A July 7, 1959 4 Sheets-Sheet 1 jade/ 2AUTOMATICALLY CONTROLLED PNEUMATICALLY POWERED LUBRICATOR Filed Sept. 8,1955 July 7, 1 59 F. G. SCHWEISTHAL 4 Sheets-Sheet 2 July'7, 1959 F. G.SCHWEISTHAL 2,393,515

AUTOMATICALLY CONTROLLED PNEUMATICALLY POWERED LUBRICATOR Filed Sept. 8,1955 4 Sheets-Sheet 3 y 1959 F. G. SCHWEISTHAL 2,893,515

AUTOMATICALLY CONTROLLED PNEUMATICALLY POWERED LUBRICATOR Filed Sept. 8,1955 4 Sheets-Sheet 4 United States Patent AUTOMATICALLY CONTROLLEDPNEUMATI- CALLY POWERED LUBRICATOR Frederick G. Schweisthal, Skokie,Ill., assignor to Stewart- Wamer Corporation, Chicago, 11L, acorporation of g n Application September 8, 1955, Serial No. 533,062

7 Claims. (Cl. 184-15) bilities, including among others-a capacity tooperate v with complete safety in an explosive atmosphere, an extremelyfast cyclic action, quiet operation, and an extended service life. Arelated object is to provide lubricating apparatus, as recited in theprevious object, which affords worthwhile economies of manufacture.

Another object is to provide automatic lubricating apparatus of theabove character which is well adapted for remote control in that it isrendered fully operative as an incident to the supplying of operatingair to a supply line to the apparatus and fully inoperative uponbleeding of air from the supply line.

Other objects and advantages will become apparent from the followingdescription of the form of the invention illustrated in the drawings, inwhich:

Figure 1 is a plan view of automatic conveyor lubricating apparatusincorporating the invention;

Fig. 2 is a side view of Fig. 1;

Fig. 3 is a vertical sectional view taken along the irregular line 3-3of Fig. 1;

Fig. 4 is a fragmentary horizontal sectional view on an enlarged scaletaken along the line 44 of Fig. 3;

Fig. 5 is a fragmentary vertical sectional view on an enlarged scaletaken along the line 5-5 of Fig. l; and

Fig. 6 is a fragmentary vertical sectional view taken generally alongthe line 6-6 of Fig. 2. Various specific components of the lubricatingapparatus forming the illustrated embodiment of the invention areessentially the same as structural counterparts in the lubricatingapparatus disclosed in the previously mentioned Patent No. 2,696,277.Since reference may be made to this patent for a detailed description ofsuch components, the description here will be confined, where possible,to a more general pattern adequate for an understanding of the presentinvention.

Specially adapted for automatically injecting charges of lubricant intothe successive grease fittings 10 on the bearings of a continuous seriesof endless conveyor wheels 12, Figs. 2 and 3, the illustrated embodimentof the invention is preferably constructed substantially as a fullyintegrated unit including an I-beam track member 14 adapted to beinstalled as an integral segment of the regular trolley track structurefor the conveyor wheels. The regular trolley track structure (not shown)is essentially similar to the track member 14.

The track member 14 of the preassembled lubricating unit providessupport to a central lubricant reservoir 16 2,893,515 Patented July 7,1959 fixed to the upper side of the track member to supply lubricant totwo automatic lubricant injecting assemblies 18 mounted on opposite endsof the track member. Only one lubricating assembly 18, designed toinject lubricant into the fittings 10 for the wheel bearings on one sideof the track member 14 is shown in the drawings, Figs. 1 to 3, as thisis adequate for an understanding of the invention. The other assembly,designed to inject lubricant into the fittings 10 on the opposite sideof the track member 14, is essentially identical to the assembly 18shown except for certain components formed substantially as mirrorimages of the illustrated structure.

Constructed essentially as described in the previously mentioned PatentNo. 2,696,277, the lubricant reservoir 16 contains a supply of lubricantmaintained under pressure by air supplied to the upper end of thereservoir, Figs. 1 and 2, through a conduit 20 leading from aconventional pressure regulating valve 22 connected to a high pressureair line 24. The pressure of air applied to the reservoir 16 isindicated by a conventional pressure gauge 26 connected to the valve 20.

The lubricant injecting assembly 18 shown is supported on the trackmember 14 by a base frame 28 adjustable laterally with respect to thetrack member, Fig. l. Formed as a unitary casting, the base 28 definesat opposite ends slots 30 which are elongated perpendicularly to thetrack member 14 to adjustably receive lag bolts 32 extending downwardlyinto supports 34, Fig. 2, secured to the track member 14, Figs. 1, 2 and3.

A laterally elongated, upwardly extending boss 36 formed on onelongitudinal side of the base frame 28 with reference to the trackmember 14near the end adjacent the lubricant reservoir 16 is centrallybored to support means which journals the upper end of an elongatedsupport arm 38, Figs. 1 to 3, for swinging movement in a vertical planeparallel to the track member. The lower end of the arm 38 supports themedial portion of a generally horizontal lubricant ejector or gun 40extending through the arm and including a lubricant dispensing nozzle42, Fig. 3, extending toward the track member 14 in general verticalalignment with the adjacent grease fittings 10 for conveyor wheels 12traveling on the track member.

Lubricant is supplied continuously to the gun 40 by a flexible conduit44 connected between the gun and a lubricant outlet 45 in the reservoir16, Fig. 2. The conduit 44 has sufiicient slack to permit freehorizontal swinging movement of the gun by the arm 38. The detailedconstruction of the gun 40, as such, is described in the previouslymentioned Patent No. 2,696,277.

Each operating cycle of the lubricating apparatus 18 begins, as shown inFig. 2, with the lubricating gun 40 and the lower end of its support arm38 displaced horizontally somewhat from a vertical plane extendingthrough the upper pivoted end of the arm in a direction from the planeopposite to the normal direction of movement of the conveyor trolleywheels 12 along the track member 14. The direction of movement of thetrolley wheels is indicated by the arrow 46, Fig. 2. A coiled spring 48,Figs. 1, 2 and 3, encircling the pivotal support means for the upper endof the arm 38 and slidably engaging at opposite ends two anchoring studs50, 52, mounted on the arm and the base 28, respectively, as shown inFig. 3 biases the lower end of the arm 38 in a direction opposite to thedirection of horizontal movement of the trolley wheels 12. Movement ofthe arm 38 is terminated at its starting position by engagement of aninwardly extending horizontal pin 54, Figs. 2 and 3, with a springcushioned stop 56 mounted in a depending pro jection 58 on the adjacentside of the base 28.

As each trolley wheel 12 on the side of the track member 14 adjacent thelubricating gun 40 moves horizontally past the starting position of thegun, the wheel is biased outwardly toward the gun by a horizontal leafspring 59 riveted or otherwise fixed at one end, Fig. 2, to the verticalweb portion 61 of the track member, Fig. 3, at a substantial distancefrom the starting position of the lower end of the arm 38 in a directionopposite to the horizontal direction of movement of the trolley wheels.The opposite end of the spring 59 slidably engages the track web 61. Thecentral portion of the spring extending horizontally past the startingposition of the gun 40 is bowed outwardly toward the gun.

Upon movement of a conveyor trolley wheel 12 across the track member 14into general horizontal alinement 'with the gun 40, Fig. 2, theperiphery of the wheel is engaged somewhat above and ahead of the wheelaxis by a rider 60, Figs. 1 to 3, extending from the lower end of thearm 38 horizontally inward toward the track member 14. As shown, therider 60 is supported in a slot 62, perpendicular to the arm 38, formedin an car 64 integral with the lower end of the arm and extendingperpendicularly therefrom in the direction of movement of the wheels 12along the track member 14.

Upon installation of the lubricating apparatus, the wheel rider 60 isadjusted in the slot 62 by means of a screw 66, Fig. 2, to efiect agenerally horizontal alignment between the lubricating gun nozzle 42 anda lubricant fitting for a wheel 12 when the rider 60 is in contact withthe wheel. The rider 60 is fixed in the slot 62 by tightening lock nuts68 on the rider, Fig. 1, against opposite sides of the support 64. Thegun 4-0 is preadjusted horizontally and vertically with respect to thearm 38 by adjusting screws 70 and 72 in the arm, Figs. 1 to 3.

Continued movement of a trolley wheel 12 along the track member 14 afterengagement of the wheel with the rider 60 swings the lower end of thearm 38 and the gun 40 away from starting position in a generallyhorizontal arc in which the lubricating nozzle 42 travels in substantialalignment with the grease fitting 10 for the wheel. In this connection,it is noteworthy that the structure supporting the gun 40 on the arm 38(as described in Patent No. 2,696,277) provides radial flexibility inthe support to the gun to compensate for the difierence between thearcuate motion of the support arm and the linear movement of theadjacent grease fitting.

After traveling a predetermined distance with the engaged Wheel 12, therider 60, swinging about the pivoted upper end of the arm 38 as acenter, clears the wheel allowing the spring 48 to return the arm tostarting position.

As the support arm 38 swings with a trolley wheel in engagement with therider 60, the lubricating gun 40 is advanced toward the track member 14to engage the nozzle 42 with the grease fitting 10 for the wheel andinject a shot of lubricant into the fitting. The gun 40,

described in the previously mentioned Patent No. 2,696,277, efiects thisaction upon the application of force to the outer end of a plungerelement 74 of the gun projecting from the side of the arm 38 oppositethe track member 14, Fig. 3.

As shown, the plunger element 74 is moved from the position shown insolid lines in Fig. 3 to the position shown in phantom in the samefigure by the lower end of a rocklever 76 medially pivoted to ahorizontal projection 78 integral with the central portion or" the arm38. The upper end of the lever 76 is forced outwardly, to accomplishthis action, by a horizontal plunger 80 extending through the upper endof the lever 38 and through the support boss 36 into overlying relationto the base 28, Figs. 1-, 3 and 4.

Actuation of the plunger 80 to operate the lubricating gun 40, as anincident to the swinging of the arm 38 away from starting position, iseffected by improved means pneumatically powered and fully controlledme-,

chanically to improve the overall operational capabilities of thelubricating apparatus as will presently appear.

More particularly, the plunger is reciprocated in timed relation toswinging movement of the arm 38 away from its starting position, Fig. 2,by operation of a mechanically controlled pneumatic actuator assembly 82adjustably positioned on the base 28, Figs. 1 and 4. The Working partsof the pneumatic actuator assembly 82 are mounted in a rectilinear body84, Figs. 1 and 4, secured in a pre-adjusted position on the base frame28 by four lag bolts 85. p I

As shown in Fig. 4, the body 84 defines and supports a horizontalcylinder and piston assembly 86 extending substantially therethrough incoaxial relation to the plunger 80. A most efiicient pneumatic controlof the piston and cylinder assembly 86 to actuate the plunger 80 isprovided by an inlet and exhaust valve assembly 88 extendingsubstantially through the body 84 in parallel relation to the piston andcylinder assembly 86 to be mechanically operated by control structure onthe swing able arm 38 with a snap action that is independent of thespeed of movement of the arm.

The piston and cylinder assembly 86 comprises a piston stem 90 axiallyaligned with the plunger 80 and making abutting contact at one end withthe plunger. From the plunger the stem 90 extends into a horizontal bore92 within the body 84, passing through a centrally bored cap 94 threadedinto a counterbore 96 in the end of the bore 92 adjacent the plunger 80.A seal between the cap 94 and the plunger 90 extending slidablytherethrough is formed by suitable packing 98 fitted around the plungerin a counterbore 100 in the inner end of the cap. The packing 98 iscompressed by a washer 102 held against the packing by one end of ahelical spring 104 coiled around the stem 90 and extending away from thecap 94 through the bore 92. p

The end of the spring 104 opposite the Washer 102 engages an enlargedpiston 105 fixed to the end of the stem 90 opposite the plunger 80. Asshown, the piston 105 comprises an annular seal 106 sandwiched betweenan annular retainer 108 and suitable pressure applying washers 110. Theretainer 108 is held firmly against an annular shoulder 112 on the stem90 by axial pressure applied to the washers by a nut 114 of substantialsize and length threaded onto the extreme outer end of the stem 90opposite the plunger 80.

The piston 105 is slidably contained in a horizontal cylinder 116 formedin effect as a large counterbore of the previously mentioned bore 92extending substantially half way through the block 84 from the sideopposite the plunger 80.

An air chamber 118 slightly larger in diameter than the cylinder 116 isformed at the outer end of the cyl-inder by counterboring the cylinderfrom the outer end to a depth somewhat less, as shown, than the axiallength of the piston nut 114.

The outer end of the cylinder 116 as continued by the air chamber 118 isclosed by a cap 120 secured to the body 84 by lag bolts 122.

To actuate the plunger 80 for efiecting movement of the lubricating gun40 through an operating cycle in the manner described, the air chamber118 is connected to a supply of operating air under pressure and toexhaust in rapid succession by the previously mentioned valve assembly88, to be described presently in detail. Air entering the chamber 118under pressure forces the piston 105 quickly to the opposite end of theCylinder 116 thus acting through the stem 90, plunger 80, and rock lever76 to engage the lubricating gun 40 with an aligned grease fitting 10and inject a charge of lubricant into the fitting. Exhausting of airfrom the chamber 118 allows the spring 104 to shift the piston 105 backto starting position freeing the lubricating gun -40 to retract from theserviced grease fitting ,10.

lien-action of the gun '40 from the grease fitting is effected byinternal spring structure of the gundescribed in the previouslymentioned Patent No. 2,696,277;

The comparatively quiet pneumatic actuation of the piston 105 through anoperating cycle is further silenced by bringing the piston to acushioned stop at opposite ends" of its reciprocable movement. For thispurpose a rubber annulus 124 is fitted into a radially enlargedannularrecess 126 at the inner end of the cylinder 116 to noiselesslyterminate inward movement of the piston 105. Also, a circular rubber pad128 is .fitted into a circular recess 130 in the inner face of the cap'120 to noiselessly stop the return movement of the piston.

Quiet breathing of the space within the bore 92 and cylinder 116inwardly of the piston 105, as an incident to reciprocation of thepiston, is provided by a muted breather passage, indicated generally bythe numeral 132, intersecting the bore 92 between the cushion 124 andthe counterbore 96. As shown in Fig. 4, the passage 132 comprises ahorizontal bore 134 entering the bore 92 from the side adjacent thelubricant reservoir :16. The bore 134 is counterbored from the outer endto a much larger diameter, forming a muting chamber 136 partiallycovered at the extreme outer end by an annular ring 138 secured to thebody 84 by lag bolts 140. q

The air chamber 118 is connected to the control valve 88 by an obliquehorizontal bore 142, Fig. 4, extending from the air chamber to anannular space 144 encircling a horizontal valve sleeve 146 fitted into abore 148 extending substantially half way through the block 84 from theside opposite the plunger 80. Air under pressure is supplied to theouter end of the bore 148 through a conduit 150 connected to an elbow152 threaded into the outer end of the bore.

Thepneumatic actuator air supply bore 142 is connected to either thehigh pressure air supply in the outer end of the bore 148 or to exhaustby the snap action of a reciprocable flow control element 154 cooperablewith the valve sleeve 146. The inlet end of the valve element 154 isformed by a spherical valve closure member 156 separably engageable withthe upstream side of an annular valve seat 158 of truncated conicalshape formed at the inlet end of the sleeve 146 and opening toward theair supply fitting 152. The valve closure member 156 is urged towardengagement with the seat 158 by a helical spring 160 having a small endengaging the valve member and a large end engaging the inner end of thefitting 152.

The spherical valve closure member 156 is welded to the adjacent end ofa cylindrical stem portion 162 of an axial connecting member 163 of thevalve element 154 extending through an axial bore 164 in the valvesleeve 146. The bore 164 is counterbored 166 from the valve seat 158past the longitudinal center of the sleeve 146. Communication betweenthe counterbore 166 and the space 144 surrounding the sleeve 146'isestab lished by two radial bores 170 in opposite side walls of thesleeve.

The end of the counterbore 166 opposite the valve seat 158 providesradial support to a square guide 172 centrally formed on the valveelement connecting member 163. The spaces between the square peripheryof the guide 172 and the inner cylindrical surface of the counterbore166 provide for the flow of air axially through the counterbore aroundthe guide.

A second stem portion 174 of the valve element connecting member 163extends from the guide 172 through the sleeve bore 164 in a directionopposite from the spherical closure member 156. The diameter of the stem174 is substantially less than that of the surrounding cylindricalsurface of the bore 164 thus providing for free flow of air along thestem through this portion of the bore.

The end of the stem 174 opposite the guide 172 connects with a secondspherical valve member 176 having a diameter substantially less(approximately one-half, as

shown) than that, of the spherical valve member 156. The smaller valvemember 176 opposes an annular valve seat 178 of truncated conical shapeon the sleeve 146 encircling the end ofthe bore 164 opposite the valveseat 158.

The overall length of the axial connecting member 163 of the valveelement 154 is sufiicient to preventthe closure members 156 and 176 fromsimultaneously engaging the respective valve seats 158:and 178: In fact,the length of the connecting member 163 j is such as to force one of thespherical valve members into open position when the'other valve memberis in closed position.

As will presently appear. the valve element 154 is shifted reverselybetween two extreme operating positions with a snap action having anoperating speed entirely unafiected by the operating speed of extremelysimple actuating structure for the valve element;

Mechanical control means forthe valve element 154 are mounted in a smallbore 180 in the block 84 axially aligned with the bore 148 andcounterbored to a substantially larger diameter 182 from the side ofthe. block adjacent the plunged 80. An annular shoulder 184 formed onthe block 84 at the juncture of the bore 180 with the bore 148 providessupport to the adjacent inner end of the sleeve 146.

A mount for the valve element operating structure is provided by acentrally bored sleeve 186 threaded into the outer end of thecounterbore 182 and held inan axially adjusted position by a lock nut188 threaded onto the sleeve for engagement with the block 84. Thesleeve 186 provides support to an axially slidable plunger 190 extendingthrough the sleeve and having an enlarged head 192 on its inner endengageable with the inner end of the sleeve. The enlarged plunger head192 is internally threaded axially to receive the threaded end of a stem194 extending from the plunger toward the valve member 176.. The stem194 is locked in an axially adjusted position on the plunger head 192 bya lock nut 196.

A helical compression spring 198 encircling the inner end of the stem194 reacts at opposite ends of the lock nut 196 and the spherical valvemember 176 respectively to urge the latter toward the valve seat 178.

As will be more clearly developed presently in connection with theoverall operation of the apparatus, the axial position of the valveelement 154 in relation to the sleeve 146 is determined by thedifferential force of the opposed springs 160 and 198 and thedifferential force of air pressure acting on the valve element.

An exhaust outlet from the valve assembly 88 is provided by a horizontalbore 200, Fig. 4, opening outwardly from the, end of the counterbore 182adjacent the valve seat 178.

The end of the valve control plunger '190 projecting outwardly from thesleeve 186 is internallythreaded to receive one end of a threaded stem.202, Fig. 4, locked in an axially adjusted position on the plunger bymeans of a lock nut 204. As shown, the projecting end portion of theplunger 190 is circumferentially knurled at 206 to be held by a suitabletool while turning the stems 194 and 202 and lock nuts 196 and 204.

The free end of the stem 202 projecting from the plunger 190 opposes oneend of a horizontal control plunger 208, Figs. 4 and 6, slidably mountedin a horizontal bore 210 in an upright boss 212 on the adjacentlongitudinal edge of the base 28. 'Axial movement of the plunger 208through the bore 210 away from the stern 202 is limited by engagementwith the boss 212 of two nuts 214, Fig. 6, threaded onto the inner endof the plunger 208 and jammed together in an axially adjusted positionon the plunger.

The plunger 208 is moved inwardly toward the valve 88, Fig. 4, as anincident to swinging movement of the arm 38 away from its startingposition, Fig. 2, by a substantially pure thrust action of cam andfollower means 7 which effectively avoids the application of radialforces to the plunger tending to cause binding against the bor 210- Asshown in Fig. 6, actuating thrust is applied to the plunger 208 by theback side of a cam follower 216 mounted in the upper end of a generallyvertical lever 218. The lower end of the lever 218 is supported by ahorizontal pivot 220 for limited swinging movement in a vertical slot222 formed in a pivot support bracket 224 attached by lag bolts 226 tothe adjacent lower marginal edge of the base 28.

The end of the cam follower 216, Fig. 6, opposite the plunger 208,defines a generally conical cam follower surface 228 adapted forcoaction with a swingable cam assembly 230. The cam assembly 230 ispivotally mounted on a support 232, Figs. 1 and 2, integral with theupper end of the arm 38 and extending laterally from the arm insubstantially parallel relation to the previously mentioned ridersupport car 64.

Generally similar to its structural counterpart in the previouslymentioned Patent No. 2,696,277, the cam assembly 230 comprises a camroller 234, Fig. 6, journaled on the outer end of a link 236 swingablysupported on a-pivot pin 238 projecting from the support 232. The end ofthe link 236 carrying the cam roller 234 is biased downwardly by aspring 240, Figs. 1 and ,6, anchored to the pin 23.8. I-lowevei',downward swinging movement of the roller end of the link 236 is stoppedin a generally horizontal position by engagement of the opposite end ofthe link with a stop pin 242 on the support memhe 2 2- Upon swinging ofthe arm 38 away from its starting position (clockwise with reference toFig. 2) by engagement'of the rider 60 with a trolley wheel 12, the camassembly 230 is carried upwardly in its generally horizontal position,Fig. 6. The cam roller 234 moves across the follower 216 forcing thefollower inwardly toward the boss 212. The pivoted lever 218 absorbs theentire component of the force of the cam roller 234 on the follower 216perpendicular to the plunger 208. Hence the cam follower 216 applies asubstantially pure axial thrust to the plunger 208 which is transmittedto the valve operating plunger 190, Fig. 4.

As the arm 38 swings back to its starting position in the mannerdescribed, the cam assembly 230 moves downwardly across the cam follower216. However, the roller end of the link 236 pivots upwardly against theaction of the spring 240 to allow the cam roller 234 to pass thefollower 216 without moving the plunger 210 inwardly.

In the preferred construction shown, the lubricating assembly 18 isoperated with air supplied under pressure directly from a hollowaccumulator 246, Figs. 1 and 2, mounted on the base 28. As shown, theaccumulator 246 is connected through a T fitting 248 with the previouslymentioned conduit 150 leading to the high pressure inlet fitting 152 forthe control valve 88.

Air is supplied under pressure to the accumulator 246 by suitable airsupply means which, by virtue of the storage capacity of theaccumulator, can be of a minimized size having an effective air deliveryrate far below the instantaneous rate of air consumption by thelubricating apparatus during an operating cycle. As shown in Figs. 1 to3, the air supply to the accumulator 246 includes a conduit 250extending froma suitable connection with the accumulator to a coupling252, Fig. 1, mounted in a boss 254 on the base 28. A connecting line 256extends from the coupling 254 to a two-way control valve 258, Figs. 1and 2 which may for convenience be located at a control station anydesired distance, from the trolley lubricating unit. Hence, alubricating unit installed in an out-of-the-way overhead position can becontrolled by a valve 258 located for convenient operation from thefloor level. Air is supplied under pressure to the valve 258 through aconventional pressu e r gulator. 2 .0 a d an ir filt ring e e 2 oconventional construction connected to a highpressure air supply line264.

Having a conventional internal construction, the control valve 258 iseffective when turned to one position to connect the accumulator airline 256 to the air supply from the valve 260 and effective when turnedto another position to connect the accumulator air line 256 to exhaust.

Full remote control of the lubricating assembly 18, as an incident tooperation of the valve 258, is completed by means which renders theassembly fully inoperative upon draining of air from the accumulator 246and fully operative upon filling the accumulator with air underpressure. More particularly this action is obtained by pneumatic controlof a generally horizontal disabling lever 266, Figs. 2 and 3, mediallypivoted on a horizontal pivot 268 on the support projection 58. A spring270 coiled around the pivot 268 and reacting at opposite ends on thesupport 58 and the disabling lever 266 urges the left hand end of thelever, Fig. 2, defining a cam surface 272, downwardly into the path ofreturn movement of the pin 54 incident to swinging of the arm 38 back tostarting position. Hence, unless restrained, the arm 266 swings towardthe position indicated in phantom in Fig, 2, for engagement with the pin54 to hold the arm 38 in an inoperative position in which the rider 611clears the trolley wheels 12.

The disabling lever 266, however, is rendered inoperative as an incidentto the supplying of operating air under pressure vto the accumulator246. 'For this purpose a piston and cylinder assembly 274, Figs. 1, 2, 3and 5, is mounted in overlying relation to the end of the lever 266opposite the cam 272 by a plate 276 supported on the base 28.

As shown, the assembly 274 comprises a vertical piston stern 278extending downwardly into abutting engagement with the underlying edgeof the lever 266. The upper end of the stem 278 is connected to a piston280, Fig' 5, slidably mounted in a cylinder 282 formed in a sleeve 284threaded into a circular base 286 mounted on and extending downwardlythrough the support plate 276. The upper end of the cylinder 282 isconnected by an elbow fitting 288 and an air supply tube 290, Figs. 1,2, 3 and 5, to the outlet T 248 from the accumu later 246.

Hence, upon operation of the valve 258 to fill the accumulator 246 withair under pressure, air flows through the conduit 290 into the cylinder282 to force the piston 280 and stem 278 downwardly against thedisabling lever 266, This immediately swings the disabling lever to itsinoperative position, shown in solid lines in Fig. 2, allowing thespring 48 to return the arm '38 to starting position for normaloperation.

Upon installation of the lubricating unit thus provided, a properlongitudinal adjustment of the lubricating gun 40 in relation to thegrease fittings 10 for the trolley wheels 12 is effected by adjustingthe base 28 laterally on the track member 14. This adjustment isprovided for by the previously described base slots 30 which receive thehold-down bolts 32.

The lubricating gun 40 and the rider 60 are adjusted on the arm 38 inthe manner described for proper engagement with each successive trolleywheel 12 and lubricant fitting 10 passing along the adjacent side of thetrack member 14.

Adjustment of the axial stroke of the lubricating gun 40 in relation tothe support arm 38 is provided for by adjusting the pneumatic assembly82, Fig. 1, toward or away from the upper end of the arm 38., Adjustmentof the assembly 82 toward the arm 38 is facilitated by an adjustingscrew 292 threaded through a support boss 294 on the side of the base 28opposite the arm support boss 36 and engaging a depending abutment 296,Fig. 3, formed on the pneumatic cylinder cap afiixed to the adjacentside of the pneumatic assembly block 84. Ad-

seat 158.

justment of the pneumatic assembly 82 in the opposite direction isfacilitated by a horizontally adjusting screw 298, Figs. 1 and 3,threaded into an upwardly extending lug 300 on the base 28 and engagingthe lower end of an abutment member 302 held against the side of theblock 84, Figs. 1, 3 and 4, by the previously mentioned cap 94. Afteradjustment of the pneumatic assembly 82, the lag bolts 85 are tightenedto maintain the block 84 in fixed position on the base 28.

The control valve 88 is fully adjustable to assure proper operation inservice. The residual stress on the spring 198, Fig. 4, when theoperating plunger 190 is in its outwardly extended position shown, isadjustable by varying the axial adjustment of the threaded sleeve 186 inthe counterbore 182. The outer end of the sleeve is knurled for thispurpose.

The degree to which the spring 198 is compressed by inward movement ofthe plunger 190 can be varied by adjusting'the position of the threadedstem 194 in the plunger head 192. The maximum compression of the spring198 is limited by engagement of the inner end of the stem 194 with thespherical flow control member 176.

The extent to which the valve control plunger 190 is moved inwardly byengagement of the cam assembly 230 with the cam operator 216, Fig. 6,can be varied by adjusting the axial position of the threaded stern 202,Fig. 4, in the outer end of the plunger 190.

I Upon being installed and properly adjusted, the improved lubricatingapparatus embodying the present invention operates quietly withextraordinary efficiency. Upon operation of the remote control valve 258to supply air under pressure to the accumulator 246, the pneumaticcontrol assembly 274, Fig. 5, operates automatically as described todisable the member 266 allowing the lubricating support arm 38 to swingimmediately to starting position.

When the arm 38 is in starting position, the valve spring 198, Fig. 4,holds the plunger 190 in extended position, in which position the forceof the spring on the flow member 176 is relaxed. At this time the othervalve spring 160 together with the force of the air pressure at theinlet end of the bore 148 holds the larger flow control member 156 infirm engagement with the valve seat 158. The passage 142 from the airchamber 118 of the cylinder-piston assembly 86 is then connected toexhaust through the valve seat 178. The closure member 176 at this timeis held away from the seat 178 by the axial connecting member 163 of thevalve element 154.

Upon swinging of the arm 38 away from starting position by the rider 60in the manner described, the valve control plunger 190 is moved inwardlyby the cam assembly 230. This compresses the spring 198 to increase itsforce tending to move the valve member 176 to closed position. Uponengagement ofthe stem 194 with the valve member 176 by continued inwardmovement of the plunger 190, the valve member 156 at the opposite end ofthe valve element 154 is unseated from the valve Unseating of the valvemember 156 drops the force of differential pressures on the valve membertending to -move ittoward the seat 158. The strength of the spring .198compressed by inward movement of the control connecting the air supplyat the inlet end of the valve seat 158 through the passage 142 to theair chamber 118. Air rushing into the chamber 118 quickly shifts thepiston 105 to the opposite end of the cylinder 116 to operate thelubricating gun 40 in the manner described. Because of the smallereffective diameter or size of the valve seat 178 in relation to thevalve seat 158, the differential force of air pressure tending to movethe valve member 176 away from seated position, after the element 154 isshifted to admit air under pressure to the bore 142, is much less thanthe force of differential air pressure tending to hold the member 156against the seat 158 before shifting of the element 154.

.As the cam assembly 230, Fig. 6, moves past the follower 216, thespring 198, Fig. 4, moves the plunger 190 outwardly until thecompressive force in the spring acting on the closure member 17 6 isreduced to a value at which the opposite spring 160 initiates closingmovement of the valve member 156. The incipient movement of the valvemember 156 toward the seat 158 accompanied by unseating of the valvemember 176 from the seat 178 immediately accentuates the differentialair pressure on the valve element 154 which is cumulative with the forceof the spring 160 tending to move the member 156 into engagement withthe seat 158. The result is a snap action of the valve element 154 whichsimultaneously seats the valve member 156 and shifts the valve member176 to fully open position. This shuts off the supply of high pressureair from the inlet fitting 152 to the connecting passageway 142 andsimultaneously connects the open valve seat 17 8 to the exhaust outlet200.

i The spring 104, Fig. 4, then returns the piston to its startingposition, allowing the lubricating gun 40 to retract from engagementwith the serviced lubricating fitting 10.

As previously intimated, the shifting movement of the valve element 154by the differential forces of the springs and 198 operating inconjunction with the difierential air pressure on the valve elementeffects a most efiicient snap action of the valve that is not slowed bythe relatively slow movement of the arm 38, which effects a mechanicalcontrol of the valve.

Capable of operating with complete safety in an explosive atmosphere,the pneumatically powered, mechanically controlled lubricating apparatusprovided by the invention is extremely efficient yet extraordinary quietin operation.

While I have shown and described a preferred embodiment of my invention,it will be apparent that numerous variations and modifications thereofmay be made without departing from the underlying principles and scopeof the invention. I therefore desire, by the following claims, toinclude all such variations and modifications by which substantially theresults of my invention may be obtained through the use of substantiallythe same or equivalent means.

I claim:

1. Pneumatic powered apparatus for automatically injecting lubricantquietly into lubricant fittings on the successive components of passingmachine structure such as an endless conveyor, comprising, incombination, a lubricant ejector, pivoted means supporting said ejectorswingably alongside the path of movement of the structural components tobe lubricated to seek a starting position, said ejector supporting meansincluding rider means engageable with each successive structuralcomponent to be lubricated for movement by the latter to swing saidsupporting means and said ejector away from said starting position untilthe rider means moving in an arcuate path clears the structuralcomponent thus carrying the ejector through a limited distance ingeneral alignment with the component, a pneumatic actuator including apiston mounted in a cylinder and interconnected with said ejector foradvancing the latter toward the structure to be lubricated uponadmission of air under pressure to one end of the cylinder, resilient.cushioning means mounted adjacent opposite ends of said piston toquietly terminate translation of said piston at opposite ends of saidcylinder, an outwardly open breather passage connected to the end ofsaid cylinder opposite said one end, means restricting the outlet end ofsaid breather passage to form therein a muting chamber for minimizingsound incident to breathing of said cylinder through said passage uponreciprocation of said piston, means forming a supply of operating airunder pressure, an inlet and exhaust valve connected to establishcommunication between said one end of said cylinder and said air supplymeans and exhaust alternately, said valve including mechanical controlmeans therefor, and mechanical valve operating means mounted on saidswingable ejector supporting means and positioned for coactionmechanically with said valve control means as an incident to swingingmovement of said ejector supporting means away from said startingposition to eifect operation of said valve to connect said air supplymeans to said cylinder for actuation of said ejector.

2. Pneumatic powered apparatus for automatically injecting lubricantinto lubricating fittings on successive components of passing machinestructure such as an endless conveyor, comprising, in combination, alubricant ejector adapted to inject lubricant into a lubricatingfitting, means movably supporting said ejector for movement alongsidethe structure to be lubricated toward and away from a starting position,means engageable with each successive component of the structure to belubricated for moving the ejector a short distance from said startingposition in general alignment with the component, said ejectorsupporting means including means normally operable to return saidejector to starting position after each movement thereof away fromstarting position, a pneumatic actuator connected with said ejector foradvancing the latter toward the structure to be lubricated, meansdefining a control valve passageway and forming inlet and outlet valveseats encircling opposite ends of said passageway and facing therefrom,inlet and outlet valve members movably disposed in opposing relationshipto said respective inlet and outlet valve seats, connecting meansbetween said valve members dimensioned to force either of said membersinto open position away from the seat therefor upon movement of theother member into closed position against the seat therefor, meansconnecting the passageway between said valve seats to said actuator, airsupply means connected to supply air under pressure to the upstream endof said inlet valve seat, the downstream end of said outlet valve seatbeing connected to exhaust, a control member for the inlet and outletvalve members movable in relation thereto, spring means interconnectedbetween said control member and one of said valve members to be stressedvariably by movement in relation to the latter of said control member toefifect shifting movement of said valve members in unison to bringalternate ones thereof into engagement with the valve seats therefor,and means for operating said' control member in synchronism withmovement of said ejector supporting means away from the startingposition therefor to energize said pneumatic actuator to advance saidejector toward the structure to be lubricated.

3. In apparatus for automatically ejecting lubricant into thelubricating fittings on successive components of passing machinestructure such as an endless conveyor, the combination of a lubricantejector adapted for ejecting lubricant into a lubricating fitting,movable means supporting said ejector for movement along side the pathof movement of the structural components to be lubricated toward andaway from a starting position, said ejector supporting means includingrider means positioned thereon for engagement with each successivecomponent of the structure to be lubricated to be actuated by the latterto carry the said lubricant ejector for a limited distance awayfrom saidstarting position in general alignment with the moving component, apneumatic cylinder containing a piston therein connected to move saidejector toward the structure to be lubricated,

a valve for controlling operation of said piston and including meansdefining a passageway, means defining an inlet valve seat encircling oneend of said passageway, air supply means connected to supply air underpressure to the upstream side of said inlet valve seat, an inlet valvemember movably disposed on the upstream side of said inlet valve seatfor separable engagement therewith, a spring mounted to urge said inletvalve member toward engagement with said inlet valve seat, meansdefining an outlet valve seat encircling the end of said passagewayopposite said inlet valve seat, said inlet and outlet valve seats facingaway from each other, an outlet valve closure member movably disposed onthe downstream side of said outlet valve seat for separable engagementtherewith, means connecting said passageway between said valve seats tothe end of said cylinder away rom which said piston moves to actuatesaid ejector, the downstream side of said outlet valve seat beingconnected to exhaust, movable valve control means engageable-With saidoutlet valve member, a spring connected between said movable controlmeans and said outlet valve member to urge the latter toward engagementwith the seat therefor, said last mentioned spring being subjected toadditional stress upon movement of said control means toward engagementwith said outlet valve member, a connecting member extending betweensaid inlet and outlet valve members and dimensioned to hold one of saidmembers in fully open position away from the adjacent valve seat whenthe other valve member is engaged against its adjacent valve seat, andvalve operating means mounted in association with said ejectorsupporting means for movement thereby mechanically into mechanicalcoacting relation with said valve control means as an incident tomovement of said ejector supporting means away from starting position tooperate said valve control means to shift said outlet valve member intoclosed position.

4. Pneumatic powered apparatus for automatically injecting lubricantinto lubricant fittings on successive components of passing machinestructure such as an endless conveyor, comprising, in combination, alubricant ejector, means movably supporting said ejector for limitedmovement alongside the path of movement of the structure to belubricated toward and away from a starting position, said ejectorsupporting means including means for moving the latter for a shortdistance in alignment with each successive structural component to belubricated, a pneumatic actuator connected to shift said ejector towardthe structure to be lubricated, compressed air supply means including aninlet and exhaust control valve connected to said pneumatic actuator tosupply air under pressure thereto and exhaust operating air therefrom,said control valve including a mechanical control member therefor, arotatably mounted wheel carried by said ejector supporting means formovement in an are substantially intersecting the axis of the controlmember, a cam follower, and a lever pivotally supported for rotation ina plane substantially tangential to the arc defined by the wheel at itsintersection with the control member axis and connected to said camfollower to support the latter in opposing relation to said valvecontrol member and in the path of said wheel for operation thereby as anincident to movement of said ejector supporting means away from startingposition, said lever serving to oppose the lateral force of said camoperator on said cam follower thus enabling the latter to transmit asubstantially pure thrust to said valve control member for efiectingoperation thereof, the wheel being supported for pivotal movement overthe follower incident to movement of the ejector supporting means towardthe starting position.

5. Pneumatic powered lubricating apparatus for automatically injectinglubricant into lubricating fittings on successive components of movingmachine structure such as an endless conveyor, comprising, incombination, a

lubricant ejector, a swingable arm supporting said ejector for movementalongside the path of movement of the structure to be lubricated towardand away from a starting position, a pneumatic cylinder, a pistonslidable within said cylinder and connected to said ejector foradvancing the latter toward the structure to be lubricated, meansdefining a control valve passageway and forming inlet and outlet valveseats encircling opposite ends of the passageway, inlet and outlet valvemembers movably disposed in opposing relation to said respective inletand outlet valve seats, connecting means between said inlet and outletvalve members dimensioned to shift either of said members into fullyopen position away from the valve seat therefor upon movement of theother member into engagement with the seat therefor, means providingcommunication between the intermediate portion of said passagewaybetween said valve seats and the end of said cylinder away from whichsaid piston moves to shift said ejector toward the structure to belubricated, reciprocable control means for said inlet and outlet valvemembers, a spring connected between said control means and one of saidvalve members for actuating the latter in response to reverse movementof said control means, translatory guide means supporting said controlmeans for reverse movements thereon, a cam follower lever pivotallysupported at one end, a cam follower mounted on the opposite end of saidlever in opposing force transmitting relation to said control means, acam control mounted on said ejector supporting arm for engagement withsaid cam follower as an incident to swinging movement of said arm awayfrom said starting position to efiect pneumatic operation of saidactuator to advance said ejector toward the structure to be lubricated.

6. Pneumatic powered apparatus for automatically ejecting lubricant intolubricating fittings on successive components of moving machinestructure such as an endless conveyor, comprising, in combination, alubricant ejector adapted for coaction with a lubricating fitting,movable means supporting said ejector for movement through a limiteddistance alongside the path of movement of the structural components tobe lubricated toward and away from a starting position, the ejectorsupporting means including rider means engageable with each successivestructural component to be lubricated for movement through a limiteddistance therewith to move said ejector away from said starting positionin substantial alignment with the component, a pneumatic cylinder havinga piston therein interconnected with said ejector for advancing thelatter toward the structure to be lubricated, means defining an inletand exhaust valve passageway and forming an inlet valve seat and anoutlet valve seat encircling opposite ends of the passageway, said valveseats facing away from each other, the end of said passageway openingthrough said inlet valve seat being substantially larger in transversesectional area than the end of the passageway opening through saidoutlet valve seat, inlet and outlet valve members separably engageablewith said inlet and outlet valve seats respectively, a connecting memberextending through said passageway in guided relation thereto andengaging at opposite ends said inlet and outlet valve members, saidconnecting member being dimensioned to move either of said inlet andoutlet valve members into open position away from the adjacent valveseat when the other valve member is moved into seated position againstthe adjacent valve seat, spring means interconnected with said inletvalve member to urge the latter toward engagement with said inlet valveseat, air supply means connected to supply air under pressure to saidinlet valve seat at the upstream side thereof, passage means connectingsaid passageway between said inlet and outlet seats to the end of saidcylinder from which said piston moves to force said lubricant ejectortoward the structure to be lubricated, the downstream side of saidoutlet valve seat being connected to exhaust, control means for saidinlet and exhaust valve members movable into engagement with the outletvalve member to force the latter toward engagement with the valve seattherefor, a. spring connected between said valve control means and saidoutlet valve member to urge the latter toward closed position againstthe valve seat therefor, said last mentioned spring being stressedincreasingly upon movement of said valve control means toward saidoutlet valve member, and mechanical operating means mechanicallyconnected with said ejector supporting means for movement thereby andpositioned to mechanically actuate said valve control means to shiftsaid outlet valve member into closed position as an incident to movementof said ejector supporting means away from starting position.

7. Pneumatic powered apparatus for automatically injecting lubricantquietly into lubricant fittings on the successive components of apassing machine structure such as an endless conveyor comprising, incombination, a lubricant ejector, means movably supporting said ejectorfor limited movement alongside the path of movement of the structure tobe lubricated and for lubricating engagement with the fittings in apredetermined position of the ejector in its path of movement, ridermeans engageable with each successive structural component to belubricated for moving the ejector in alignment with the fitting, apneumatic actuator including a piston mounted in a cylinder andinterconnected with the ejector, resilient cushioning means mountedadjacent opposite ends of said piston to quietly terminate translationof said piston at opposide ends of said cylinder, an outwardly openbreather passage connected to one end of said cylinder, meansrestricting the outlet end of said breather passage to form therein amuting chamber for minimizing sound incident to breathing of saidcylinder through said passage upon reciprocation of said piston, meansforming a supply of operating air under pressure, an inlet and exhaustvalve connected to establish communication between the other end of saidcylinder and said air supply means and exhaust alternately, said valveincluding mechanical control means effective in a predetermined positionof the ejector to connect said air supply means to said cylinder foractuation of the ejector.

References Cited in the file of this patent UNITED STATES PATENTS1,704,238 Barks Mar. 5, 1929 2,048,323 Cutts July 21, 1936 2,264,649Tebaldi Dec. 2, 1941 2,502,659 Livingston Apr. 4, 1950 2,696,277Schweisthal et al. Dec. 7, 1954 2,699,756 Miller Jan. 18, 1955 FOREIGNPATENTS 571,844 Great Britain Sept. 11, 1945

